Transmission

ABSTRACT

A module comprising at least the groupings ( 11 ) and ( 12 ) which remains the same for all embodiments. Assemblies ( 11 ) and ( 12 ) are effectively side by side unequal co-axial assemblies. Assembly ( 11 ) is the unequal coaxial assembly and comprises of a cam [sun-element] ( 17 ), bearing ( 18 ) and rollers [planet-element] ( 20 ). Assembly ( 12 ) is the second unequal coaxial assembly and comprises of a rotor ( 15 ), cam [sun-element] ( 16 ) and rollers [planet-element] ( 19 ) being constrained with the planet elements of the assemblies and body ( 45 ) within the body element ( 21 ) of assembly ( 11 ).

This invention relates to devices for the transmission of mechanicalpower in the form of rotational motion. In particular, it is directed totransmission of power between a first rotationally movable element and asecond rotationally movable element to provide a device which canprovide, in a preferred form, continuously variable ratios, of angularvelocity at an input to angular velocity at an output, within the rangeof ratios −1:1 to 0 to +1:1.

The present invention finds use in electronic, hydraulic or mechanicalapplications and, in a preferred form, provides variable input andoutput speeds; an output angular velocity that varies from 0 to + thegear ratio as the input varies from zero to the input angular velocity;torque multiplication; the ability to vary speed and torque.Furthermore, the present invention provides multiple inputs and/oroutputs and reduction, step up or 1:1 gear ratios. This invention,includes the use of a planetary drive, that is a drive which includes aset of rollers, bearings or similar moveable parts, arranged in a circlearound an axis and configured so that, through their movement inconcert, apply torque to a body whose resultant rotation is used as theoutput of the drive. Examples of similar drives are described inAustralian Patents 607822 and 613927 as spin control differentials forvehicles and couplings. A planetary drive based on a sun gear, a ringgear, and a planetary gear carrier is disclosed in Australian Patentnumber 465202 in the name of Eaton Corporation.

Examples of planetary drives are manufactured by Sumitomo Heavyindustries Ltd, Japan, under the name “Cyclodrive”. Although planetarygears are known, the prior art gears have failed to take advantage ofcertain of their features, in particular, the contra-rotational natureof the input and output shafts being on the same axis.

This present invention advancement is a “Transmission” (referred to asan “eM Dean” sometimes) having at least one input and one output andbeing of the epicyclic type involving interaction of three mechanicallydistinct rotating elements with any suitable form that allows thetransfer of torque between input and output, namely a sun element, aring element and a planet element in each of at least first and secondunequal co-axial epicyclic assemblies, a first element of the firstassembly and a first element of the second assembly able to rotateindependently, the first element of the second assembly within the firstrotating element of the first assembly, a second rotating element of thefirst assembly and a second rotating element of the second assemblybeing constrained to rotate at a common angular velocity, a thirdelement of the first assembly being connected to a motive source, andcontrol means for progressively changing the gear ratio applied to aload connected to the first element of the first assembly of thetransmission, (referred to as an “eM Dean” sometimes or Variable RatioMulti-gear sometimes) characterised in that the first and secondassemblies each represent unequal fixed gear ratios respectively betweenthe input and the output of the transmission, (Variable RatioMulti-gear,) the first and second assemblies arranged so that ifindividually each assembly has their first element constrained and theirthird element rotated in a certain direction the second element will tryto rotate in an opposite direction relative to the tendency of the otherassembly, the control means being operative to progressively increase ordecrease the output gear ratio in accordance with the demand for anoutput lower or higher gear stage of operation.

Alternatively the roller gear is described following, wherein the firstelements are the ring elements of the respective assemblies, the ringelements being outer bodies having spaced endless scallop guides beingadapted to receive sets of planet elements being in the form of rollers,the second rotating elements comprising of planet carrier elements andplanet elements, the planet carrier elements of the respectiveassemblies constrained to rotate about an axis collinear with the axesof their respective third elements, the planet carrier elements locatingand controlling the motion of integral spaced sets of rollerscorresponding to the planet elements of each assembly, the rollersbridging between the scallop guides of the outer bodies and the thirdelements of the assemblies, the planet carrier elements beingconstrained by a rotation controlling means allowing free rotation inone direction and a controlled rotation in the other direction, thethird elements of the assemblies being sun elements in the form ofrespective cams. This new advancement of having an internal Body nowwithin another is described below under the relevant wording whichrefers to it is as follows.

It describes my present older Patent designs with ring-gears being “sideby side” as can be seen in the cross section drawing of FIG. 2 whichmore clearly explains the FIG. 1 in all these Patent drawings. FIG. 1shows the variable options with internal—either single electric ordouble contra-rotation and further optionally three rotor electricalcontrol variations. The electrical coils were then shown as withmultiple hypothetical abilities, with FIG. 2 explaining the practicalnecessities as to how the ring-gears would be physically constructed forthe optional external one or more or combined power sources such as forHybrid applications as well.

The Electrical options are described on page 9 from lines 18 in thePC/02/00305 as follows—The magnetic effects caused by item (25) candrive the cage (22) with the same action as (23) does on item (14) Thetorque caused by items (25) would need to be higher relative to thetorque required by the cams (16) and (17) and so the electric coils arean ancillary action and not necessary for the central concept of thepresent invention. Although it is necessary for some applications toinclude it. This is for such as storage of energy by electronic and/ormechanical control as described further on.

With any means of reverse rotation restriction of the carrier being ableto implement a first torque transition to the load. This is when aninput rotation is applied to the cam (sun gear). This third rotorcoupled to the double carrier (22) is so long in FIG. 1 thus able to beactuated alternatively by a ground reference one way restriction orwhere accumulation of energy is able to be accessed. The groundreference is shown with the shaded area of the housing. In order to moreeasily see how energy storage is actuated we can refer to the firstPatent Windmill experiment. Several alternative methods have beendescribed with some trailed, within the previous pages, in divisionalPatent 2003204953 (from AU 93246/98) There is described how by placing asmall wind turbine blade on the input cam (sun gear), being the firstinput; say at 1 to 6 ratio. There can be a simple storage of energyprovided in a simple three component epicycle configuration of gearing.This was described by having another large heavy turbine blade on thereverse rotating cage (carrier).

At low wind speed the heavy load coupled to the body (ring-gear wouldnot be able to be turned because of the high torque necessary. Insteadthe large heavy blade would be forced to rotate in the oppositedirection to its designed pitch. Thus being forced into the oppositedirection thus gaining momentum (against the wind) to its normaldirection. It would turn when the wind increases for its designed“Pitch” for turning the load, this is because of the reduction gearing.As the wind increases the large blade slows slightly from reversing, dueto the designed “pitch”. Immediately the added torque from both thefirst small wind turbine blade together with the momentum developed bythe reverse rotating large blade reproduces the recovered storage ofenergy able to now provide enormous torque to start the load rotation.Eventually the load will turn faster than either of them and the loadwill also turn faster than both them, the two input rotation speeds willbe added together on the load.

The duty cycle of the windmill is thereby increased substantially notonly because it could absorb useless recoverable energy but it overcomesthe common problem of the unpredictability of sufficient wind to evenjust get a load started. Sometimes there will never enough wind to evenbe strong enough to start a windmill for days. Whereas this can now makethe difference between even the viability of wind power. The otheradvantage with this transmission is that we now can have much smallerblade diameters because of our optional contra-rotating blades, togetherwith the coupling with the higher torque such as with the Compact TorqueMultiplier herewith as described below. Multiple windmills can now fitside by side on one tower. Similarly Solar energy systems, such as fordriving pumps have initial starting frictional load features toovercome. By having some simple mechanism which would similarly work ona reverse Epi-cyclic reduction gear component against a ground reference(which the large windmill blade could be likened to or indeed haveintegrated with it by including a one way clutch to a ground reference).However in this situation a coiled torsion spring or a heavy weighthanging on a cable could be used instead of the large heavy blade. Byclever design there can be a resetting coiled spring locking onto ashaft which could allow the following to provide even more torque andenergy storage. This can be very simple just to give a load a kick off.

The next step to understand this invention was the providing of a “verycompact Torque Multiplier” this is done by adding a double Cage(Carrier) and a fourth Planetary Component, being another cam(sun-gear).—(not including the rollers etc which are needed). Thispresent new Patent Application Epi-cyclic design is now advancing thisinvention where one body is within another, not side by side as all myothers were. Where it is needed to drive any wheel, this requires thatthe output is accessible to optionally act as the wheel hub and soobviously to be the outside ring-gear and around the other ring gear,which being a smaller lower power roller is now within it.

One Patent Attorney suggested that we may attain an even earlierpriority date from even this present Patent Application if it is takenthat my previous one—PCT/02/00305 discloses this somewhat already byshowing a body within a body where the heavy output ring-gear (21) isshown within the smaller roller ring-gear in FIG. 1. This smaller rollerring-gear was only shown in this position, to show another optionalconfiguration and at the same time so as to accommodate the optionalfield coils (23,24,25) and further to show the relationship to thedouble carrier (22) relevant to everything else. Therefore it had to bedrawn at the larger diameter, this put it at (26) shown as groundreference, with a small dotted line indicating the second optionalrotating ring-gear option.

In order to further describe this invention please refer to page 2 of myDivisional Patent “Converter” AU 35198/01 which provides PoldersEpicyclic calculations. The following applies to this presentadvancement in appropriate wording and is included so as to understandthe present Claims, where any type of epicyclic gearing may be used.

There are some pertinent descriptions made in my prior Patents which cannow make this new advance clearer. Some of the earlier description canshow unique construction of this new drive now optionally using thereplaceable ring gears as especially designed to act like replaceableinserts. This is to easily change any fixed ratios if thought necessaryafter manufacturing is completed, or to change the speed of a conveyorbelt for example. Some early references are also made and described inthe “Wheels Within Wheels” Document 6-6-96 which was not availableexcept under strict confidential disclosures. Such as in item 32 whichis available by referring to Divisional Patent AU—2003204953—which wasre-applied for in year 2002 which was originally from Patent ApplicationAU 93246/98.

The drawing of FIG. 5-showing four wheel steering further becomes viablenow with this new patent advance. Having the ability to now have thefour wheel vehicle with four wheel steering and also four wheel drivebeing able to incorporate self contained motors of any type, such asElectric, Hydraulic, or Hybrid of any kind. Constant Velocity Joints canbe discarded.

Alternatively there is the ability to incorporate enormous technologicalleaps by providing “Three Dimensional” features such the kind of vehiclewhich can lean into a corner—like a motor-cycle, see FIG. 30 from thisPresent Patent Application See FIG. 12, FIG. 6, and FIG. 13.

Some of the unique uses described for this “Ultimate Transmission”invention, which can be providing every conceivable extreme requirement,I have ever required. Able to be self contained or support everything,able to integrate multiple inputs and outputs, single inputs can deliverand provide, high torque variable speed transmissions, to continuouslyvariable, to infinitely variable speed, to sequential transmissions tolikening it to operating as a type of Yo-Yo action, to lineartransmission outputs and further can be performed on one axis, or to andfrom any other axis. Able to be low cost with low wear, can be designedfor short duty cycles because nothing is moving when up to 1 to 1 ratio.As also where there is unlimited speed requirements because there onlyneed be the difference from input to output speed, it may contain itsown lubricant which can double to provide automatic governing, and easymaintenance. It is also able to use advanced materials such as ceramicsor titanium, yet sizes can be from Micro to Macro.

The great advance is that the intrinsic nature of this fixed ratio geardesign allows the multiple gearing inputs and outputs to becomedynamically interrelated, the components of all the relative referencepoints can be exploited as they are all moving relative to each other.The gear shafts can be massive where required for extremely low ratioleverage enabling the whole structure of the machines to be “alive”.

Some hybrid description of this invention given by a highly respectedMechanical Professor, he suggested it as advancement for Toyota and isvery appropriate, particularly with reference to their hybrid drives.

Many energy storage and integration of rotational force options arepossible. Governor action can further be controlled by the intrinsicdynamic nature of the transmission having fixed ratios, which maycentrifugally equalise the inputs and outputs for optimum operation.(Electronic control for optimum performance together with maximumefficiency is extremely complementary to this transmission andrelatively low cost, with manual over-riding being available).

As further understood by the Engineering Professor, a “Pulley” system hefurther explained how some of the more exciting features of the dynamiccomponent of this invention can be better understood, by labelling FIG.6 (or new FIG. 13 B herein, see drawings Page 12) as showing an“internal View” and labelling FIG. 12 as showing an “External View” (thethree dimensional view being seen for example by looking at FIG. 30,showing the car and passengers tilting into the corner like amotor-cycle instead of throwing out as would normally occur.)

There can be seen the two variable gears positioned between the twofront wheels and also between the rear wheels. Continual correction isthereby available to smooth out travel for total passenger comfort. FIG.5 lower drawing can be integrated with FIG. 12 for camber and caster.The combined advance of low cost electronic sensors can be input intolow cost Miro-processors thereby providing pre programmed reactivecorrection for any scenario and every obstacle or road irregularityencountered. This is the ultimate result which can be incorporatedtogether with linear high torque acceleration and smooth braking.

Silicone Polymers as used in shock absorbers are very complimentary andoptionally able to be used for many of the present advances. These canbe actuated again by low cost high voltage, low current electronics.

Other advanced body shapes and structures may be used such as forstrength, low wind resistance ease of manufacture. By using theextremely indestructible structural shape which may be understood as aThree in One structure which provides the minimum surface area tomaximum capacity and may be understood to have physical, scientific,chemical and spiritual dimensions and connotations. Three equilateraltriangles form the basis of this structure with the ability to viewright around in a 360-degree path in any direction in our threedimensional world, it is called a “tetrahedron.” However in order toprovide substance and capacity, we have to have a fourth side, (whichcan be positioned anywhere from infinity to infinity) this fourth sideis also an equilateral triangle. Einstein postulated that our world isthree-dimensional, where a fourth dimension can be understood as beingtime. This tetrahedron structure further can be extended into as manymore of these triangles if required thereby providing extremely strongenclosures.

For our present convenience, rectangular connecting panels for extendingfor example two of these enclosures together for example for buildinglonger high-speed vehicles and also for water transport would beoptions. After the previous advanced optional features, the following 18lines below is the wording direct from this present ProvisionalApplication. Further explaining that the old ring gear bodies had norotational movement between them except where clearly shown, beingalways positioned side by side. “The bodies of this transmission” may bemanufactured by any known method, being described as “laminated”, thescallops or ring-gear may be provided side by side in any known methodwhere there is no rotational movement in between them.

As described previously they can be inside the wheel, the scallops canbe machined inside the wheel hub, inside complete with motor, (orcontra-rotating motor). Or other epi-cyclic designs could be used wherethe bodies may be, for example within each other. Or pump combinationsmay be used without differentiating from the present invention. (Thereis the exception shown in for example in FIG. 11 where there is a flangeshowing very clearly where such a split-would be such as for fans orsimilar. However the latest Patent P.C.TAU/02/00305 do have a splitbody, but between the first epicyclic movements double carrier as analternative design). Any number of ring gear/scallops could bemanufactured in one piece, simply bolted together, or slid intorotational restricting cavities, or enclosed (see inserts to add orchange ratios in item 32 page 42 or page 71, line 21), or any otherepicyclic design may be used such as described in page 1 of thispatent.”)

With the PCT/02/00305 not only was it found difficult to seal thelubricant properly, but there was very little support available from thebody for applications needing support from one end only, this is due tothe Patent limitations if trying to claim for other than a split body.Other drives such, as AU 74784 could have claimed the ability to have aring-gear body extension to overcome the above as it has similarly theseparate ring gears. Any other Epi-cyclic (or Planetary) Gearing suchToothed or any type can have similar “Torque Multiplying” abilities aswas listed in my original first front page similarly to as copied above.It included the EATON Patent. Number on the front Patent page as now. Itfurther includes the CYCLODRIVE types of Epi-Cyclic designs described.By choosing particular configuration for the Cyclodrive type we are ableto also use them or to integrate them with my roller gear design, oralso with toothed gearing as well, with any type. Now we can have apowerful drive with everything working better because it is doing thiswithin a body. In order to be within it wasn't easy to figure out how toadd the second one way clutch working in sequence together with thefirst one way clutch referenced to ground, as it had to be built beforeit could be proven. There is the option of having another one way clutchfor motor braking, controllable or even manual, or automatic, betweenthe input shaft and output (usually being the body or a ring gear withthe roller gear option).

Where it is chosen to use one or more Pumps (instead of our own rollerdesign) we need a first carrier rotating in a reverse direction to theinput and output directions. Thereby this can be adapted for obtainingthe fundamental first powerful fixed ratio. There is needed a one wayrestriction of the carrier against a ground reference but as it willhave to be internally actuated, a second one way restriction has to besequentially actuated-from the other end. Then any chosen manner such aswith the carrier being non-rotationally coupled to another Epi-cycliccomponent to form a “Compact Torque Multiplier” configuration with thefirst pump or gear. Any means can be applied to propel the drive furtherforward by accessing the “Torque Multiplier” with such as a centrifugalclutch between the centre shaft direction and the super sensitiveoppositely rotating second sun gear, (as shown with the optionallychosen roller design drawings shown). This is in order to similarly liftthe load away in the forward direction, from the one way restriction andthis is achieved then (for example) by providing a centrifugallycontrolled variable coupling (or reduced frictional coupling). (Any typeof control to which even external or manual override can take overcontrol when chosen, may be used). This is accessing the TorqueMultiplying feature to leave the one way clutch and for advancing theload forward.

If chosen the second roller gear or any other epicyclic design can besupported by this main first Epi-cyclic gear or pump, then bysequentially operating one way restrictions, (this can all bealternatively designed totally inside the body of the first pump/gear).

Hydraulics is very complimentary to this drive. This also has the addedsimplicity of providing enormous “Regeneration” for example by havingthe internal one way action being designed to pressurise internal orexternal accumulators. These can be controlled by pressure valves andpressure sensors. Either internal automatic self regulating for a loador controlled externally. The load or loads may be controlled such ashydraulically in series for example with four (or more) wheel drivevehicles externally. Automatic control by centrifugal action is one ofthe optional features, as the demand is required by the load. Oralternatively by a simple centrifugal frictional clutching. Electroniccontrol is also optional.

Any pumping, whether from the inherent displacement within the rollerdesign or standard pumps are modified, can as well provide pressurecontrol which can be designed into the drive by discreet or cleverchannelling for providing wear free features as well, such as forreplacing the need for Frictional Centrifugal Clutches. This can alsofacilitate automatic control and governing of speed. Hydrostaticbalancing as above also for oil filtering, cooling, and also so as toform a lubricating film between contacting surfaces. This can also stopor control metal to metal wear.

In our FIG. 2 drawing there is added a second optional extension on theright hand side as advanced from the previous FIG. 2 “A Converter”Patent, which now also can have another internal Ring gear no 51 insteadof the cage (carrier) as before. The output can be taken now from thisadded output no. 51 this is by removing the two bolts with arrows shown.

Although this transmission is shown in this configuration, which mayprovide over-drives—no 52 and reversing no 50—features now. Reversing isavailable from either end by choosing suitable configurations and bybreaking these. (High torque reverse braking can be applied if anotherconfiguration of the torque multiplier is chosen at the right sideinstead of the reduction gear shown). There is the option of adding moreinputs and outputs where required. Selection of ratios can also beprovided by including different ring gears within the Body Case with theability to change ratios for example by moving the concentric selectorssideways. There is the ability to change ratios also by sliding thering-gears in or out (as also for permanent ratio changing, if chosencompletely in and out of the Body case being made as havingnon-rotational ring-gear inserts, (as described in item. 32 WheelsWithin Wheels 6-6-96.)

BACKGROUND TO THE INVENTION

Epicyclic gear trains are common. Polder describes variable epicyclicgear trains in his publication “A Network Theory for Variable EpicyclicGear Trains” published in 1969 by Greve Offset N. V. Eindhoven,Netherlands, an epicyclic gear being characterised as a black box unitwith three rotating elements which are effectively able to be consideredas shafts since any one may comprise an input or output, represented ina mathematical mode as a “three pole” device with one linear equationfor angular velocities and two linear equations for torques.

The equation for angular velocities is written in the general form andcan be seen if chosen by referring to my previous invention as follows.THIS invention relates to A CONVERTER of the epicyclic type. The presentapplication 2003204953 is a divisional of parent application No.42515/99. Polder's network theory of variable epicyclic gear trainsinvolves simplifying any epicyclic gear train into an equivalentinvolving three pole branches, usually a combination of simple threepole transmission branches and three pole epicyclic branches.

Clearly by appropriate selection of the ratios the torque and powercharacterisation of any epicyclic gear train can be determined in thissense the relationships involved in an epicyclic gear train are welldefined. Polder suggests a number of variable epicyclic gear trainsderived using his network theory. An object of the present invention isto provide an “eM Dean” gear of the epicyclic type as a usefulalternative to the prior art.

OUTLINE OF THE INVENTION

In one aspect the invention provides a transmission having an input andan output and being of the epicyclic type involving interaction of threemechanically distinct rotating elements, namely a sun element, a ringelement and a planet carrier element in each of at least first andsecond unequal co-axial epicyclic assemblies, a first rotating elementof the first assembly And a first rotating element of the secondassembly able to rotate independently, the first element of the secondassembly able to be within the first element of the first assembly, asecond rotating element of the first assembly and a second rotatingelement of the second assembly being constrained to rotate at a commonangular velocity, and control means for progressively changing the gearratio applied to a load connected to the first rotating elements of the“eM Dean” Gear characterised in that the first rotating elements areunequal pairs of the same mechanical elements of the respectiveassemblies and in conjunction with respective second rotating elementseach represent different respective fixed gear ratios relative to theinput and the output of the transmission the second rotating elementsare unequal pairs of the same mechanical elements of the respectiveassemblies and in conjunction with respective said first rotatingelements each represent fixed gear ratios between the input and theoutput of the transmission or “eM Dean” Gear a third element of thesecond assembly rotating in response to demand for an output low gearstage of operation of the “eM Dean” Gear and the control means beingoperative to progressively increase the output gear ratio and at thesame time slow the rotation of the third element in accordance withdemand for an output higher gear stage of operation, the control meansbeing operative to increase or decrease the output gear ratioautomatically in accordance with the said demand.

In the description “output higher gear stage of operations means“higher” in the sense of a gear ratio approaching 1:1 ratio as input tooutput, while “output low gear stage of operation” means an outputgearing in the opposite sense generally corresponding to a lower outputangular velocity.

The first rotating elements are typically the ring elements of therespective assemblies. The ring elements are preferably outer bodieshaving spaced endless scallop guides, each scallop guide having unequalrelative numbers of scallops to rollers in either side depending on therequired gear ratios for a particular application and the guides beingadapted to receive sets of planet rollers of the planet carrierelements.

The second rotating elements are typically the planet carrier elementsof the respective assemblies. The planet carrier elements are typicallyformed as an integral unit housing spaced sets of rollers of unequalnumbers relative to the number of scallops, with the rollerscorresponding to the planets of each assembly, the rollers bridgingbetween the scallop guides of the outer bodies and the third elements ofthe assemblies. The planet carrier is preferably constrained by arotation blocking means to travel in one direction only. The rotationblocking means is preferably a selective rotation blocking meansenabling selection of rotation of the second rotating elements inforward or reverse direction. With two rotations blocking means to workin sequence preferably reversing automatically on the internal ring-gear(45).

The third elements of the assemblies are preferably sun elements in theform of respective cams, each cam typically having a roller bearingassembly separating the cam into an inner cam and a cam ring able totravel opposite the direction of the inner cam.

The control means is typically a centrifugal clutch operable to slip topartially engage the third element of the second assembly across acontinuous range of output gear ratios between fully disengaged andfully engaged positions of the centrifugal clutch at respectivepredetermined low and high output angular velocities. Alternativelyinternal or external hydraulic or any electronic, electric, magneticcontrol, Liquid Polymer in Silicon oil can be used together with EHTvoltage with its self lubricating ability.

BRIEF DESCRIPTION OF THE DRAWINGS

Pages 1/4=FIG. 1; 2/4=FIG. 2, FIG. 13; 3/4=FIG. 5, FIG. 18(Helicopter);4/4=FIG. 12, FIG. 30.Car leaning like motor-cycle, (refer also to FIG.5) and FIG. 29A (Paraplegic Support),

FIG. 1, shows the advancement in section corresponding to prior art asfrom the original

FIG. 4A of the parent application 42515/99; having being re-drawn asFIG. 1 of Patent AU 742781 or 35198/01 “A Converter”, and also shown asFIG. 13A in AU 2003204953, being a divisional patent of 93246/98.—Withsome original detail left visible being heavily circled with pointingarrows to where the new positions of the same items are, for the newinner body (45). Option 1B shows a three rotor motor with coils andmagnets as before, but now within (21).

Option 1A shows a single rotor motor (13) and (14) with a centrifugalclutch keyed to the central shaft, working in any number of knownmethods against item (15). Governing of the load can become automatic asan inherent feature due to the “dynamic” centrifugal nature such as withthe fluid contents, providing self regulating operation. Hydraulicdesign techniques employed within or without can provide variablecouplings between (13 and (14), or other chosen component

together with built in energy storage. This can be accessed from astationary component such as a dead axle. Internal or external fluidreservoirs are extremely compatible to the intrinsic design, as also ismechanical and/or electrical regeneration.

2/4 FIG. 2 is an advancement to the above FIG. 2 “A Converter”corresponding also to FIG. 6 of prior application 42515/99 and FIG. 13Bin AU 2003204953 showing advancements

from FIG. 2 of prior Patent AU 742781 or 35198/01 “A Converter”. Someoriginal detail is retained showing the advancement being the new innerbody ring-gear, and optionally more added body extensions. There areunlimited body extensions available for multiple dynamically coupledrequirements.

Contra-rotation can provide highly manoeuvrable helicopters with smalldiameter blades together with lower centre of gravity, see FIG. 18.

FIG. 13, A and B are FIG. 1 and 2 respectively from the “A Converter”Patent above and compares the older patent with the advance herein withthe pointer lines indicating to the same item numbers used.

FIG. 30 which shows a diagonal view of “my Dream Car” which can bedriven like a motorcycle together with the same feel of leaning into thecorner. The passenger compartment is also able to be reactively tiltedtowards and into the corner. Sophisticated electronics can be low costfor smoothing out the corner. The FIG. 5 is showing a four wheelsteering for vehicles which has now become almost viable because we canhave high torque self contained motors in the wheels. (Or externallyplaced motors). The vehicle can drive straight forward and can alsodrive at right angles into the kerb to safely drop off passengers oreven just for parking. With built in motors into the wheels which may besomewhat similar to as shown in FIG. 1, if chosen. FIG. 5 has just nowbecome viable with a demonstrated working geared wheel prototype.

METHOD OF PERFORMANCE Referring to the drawings, there is illustrated inFIG. 1 and

in the left side of FIG. 2—Two eMDean Gears employing similar generalconfiguration in both, having an epicyclic unit or module showncollectively in relation to the components concerning numerals 11 and 12which is shown also as the 10 side in FIG. 2 with the numerals 11 and 12again in FIG. 1 Shown here in one form and the inclusion of this moduleto all embodiments being the central concept of the present invention.In the example illustrated in assemblies 11 and 12, these are both ofthe cycloidal type, that is, employing scallops and rollers.

While each module is shown generally with the numerals 10, 11 and 12, inFIGS. 1 and 2 the particular module used in each case differs in termsof specific arrangement due to the different applications.

Modules employed will vary in specific arrangement for otherapplications as well. What is common is that each of the assemblies 10,11, 12 shares a common planet element and a common ring element. Withthe“first ring element of the second assembly 45 able to be within thefirst ring element of first assembly 21. Where other Epi-cyclic designsare used or integrated with the roller design, the common double carriercould be coupled to the second ring-gear, for example Cyclodrive andtoothed gearing. The sun elements are separate cams, Rollers Bridgebetween the cams and the scallops. The planet element comprises a planetcarrier bridging axially-between the assemblies having opposite sideswhich are unequal in terms of the number of rollers relative to thenumber of scallops carried by the planet carrier, while the ringelements comprise outer bodies having scallops arranged so theassemblies each represent different fixed ratios relative to an inputand an output.

This means the planet carriers of the two assemblies are constrained torotate at the same angular velocity. The outer bodies of the twoassemblies are able to rotate independently in the illustratedembodiments the angular velocity of the first outer body could be zero.(Unless Rotation Blocking is actuated-see page 14. line 20, this when aninput rotation is applied).

In each assembly the cams are eccentric cams which rotate inco-operation with the scallops and roller configuration of therespective assemblies. One of the cams is driven by an input shaft; thiswill cause the output that is the outer body, to rotate while the othercam rotates in the opposite direction. The output gear ratio isinfluenced by the angular velocity of the second cam, thus variousbraking arrangements applied to the second cam will influence the outputin a controllable fashion according to demand.

While the above description deals with the general features involved thefollowing description will enable understanding of the application ofthe invention to the two specific applications of FIG. 1 and FIG. 2.

FIG. 1 shows a transmission (referred to as an “eM Dean Gear sometimes)input shaft 13 with The previous alternative rotors can now still beduplicated internally concentrically, being shown as options here andalso with dotted lines which were in the FIG. 1 “A Converter Patent AU742781, or 35198/01 according to This invention as well can apply aninput which is a rotor (14) an output (21) and electrical coil andpermanent magnet arrangements (23—25) that did apply torquesrespectively to rotors (14, 15) and a planet element in the form of acage (22).

Items 23, 24 and 25 are arrangements of permanent magnets and electricalcoils so that with electricity flowing through the coils, interactingmagnetic fields are produced which cause a torque on the rotors (14, 15)and cage (22) respectively. The electricity supply can be adjustedindividually for each of items 23 to 25.

The rotor (14) and input shaft (13) are combined as an integrated partin this module. As an alternative, the rotor (14) could be removed andthe input could be solely from an external motive source driving theinput shaft (13). The point is the module comprising the groupings 11and 12 remains the same.

Assembly 11 is the first unequal coaxial assembly and comprises of a cam{sun-element} (17), bearing (18) and rollers {planet-element} (20). Thecam (17) is fixed to the input shaft (13), which is therefore fixed tothe input. The bearing (18) has an inner sleeve fitted to the outerdiameter of the cam (17). The bearing has an outer sleeve, the outersleeve of the bearing (18) makes contact with the rollers (20). As theinput rotates, the cam (17) causes the bearing (18) to move in aneccentric fashion. This causes the rollers (20) to be cyclicallydisplaced away and towards the central axis of the MDean Gear the totaldisplacement relative to this central axis, being twice the cam axisoffset from this axis. The rollers (20) are located in equally spacedguides in the cage {planet element} (22). The rollers (20) make contactwith scallops in the output {ring element}(21). For both assemblies (11& 12), the number of scallops relative to the number rollers in contactwith the scallops, determines the direction of rotation it would rotatethe output (21) if the cage (22) was held still. One more scallop thanthe number of rollers gives an output rotation direction the same as thecam rotation. One less scallop than the number of rollers would give anoutput rotation the opposite to the cam rotation. The scallops are soshaped that as the rollers are acted on by the cam, the scallops rotaterelative to the cage at a constant angular velocity ratio to that of thecam. The action between the cam (17), bearing (18) and rollers (20)against the output (21), causes an equal and opposite reaction on thecage (22), tending to rotate it in the opposite direction to therotation of the output (21). The cage (22) is constrained by a rotationblocking means in such a way as to allow the cage (22) to only rotate ina direction the same as the output (21). Therefore because of thereactive forces, the cage (22) will be held against the rotationblocking means and will therefore be stationary relative to the frame(26) with just the actions of assembly 11 alone.

This advance is in order to provide more practical transmissions forbetter supporting a load and for better sealing even its own lubricantthan was possible with the previous “Split Body Patent”. It wastherefore necessary to advance on the previous one by putting a Bodywithin the other. (instead of the external split). This was achievedwith this present new ring body inside the main Body design.

A “Solid Body” now encloses the second body within and there is a verycompact “Torque Multiplier” design provided as a result.

However the following description can still “be related to becauseeither a single power source or contra-rotational and Hybrid qualitiesare still able to be accessed but now in a more compact and more selfsupporting advancement. With a “Motor Wheel” now being a reality. Therotors which were in previous FIG. 1 of A Converter are shown withpointer lines to both the new and old inputs, as easier to explain thisadvancement as follows. However each time there is referred to the threerotors shown, these can be replaced with a new position, but now able tobe within (or internal and external power sources can still be combinedsuch combining internal electric or hydraulic with external electric orhydraulic, such for Hybrid, where chosen).

The magnetic effects caused by items 25 can drive the cage (22) (withthe same action as 23 does on item 14. This torque caused by items 25 isan ancillary action and not necessary for the central concept of thepresent invention.)(These components are now inside the ring gear bodynow with 25 being shown now with one way clutching instead, where twoone way clutches are used in sequence to transfer the first powerfultorque to the load from a Ground Reference).

The carrier 22 can now be actuating energy storage internally by beingforced into a reversing direction to the load direction, this canprovide pumping (or even a coiled torsion spring can absorb energy) Thepumping can be integrated with internal accumulation or externalaccumulation for regeneration. There is alternatively the requirementfor two one way clutches to reference the carrier 22 to ground accessedsequentially through the internal Ring Gear 45.

The one way clutches can be similar to as described in ArthurWoodbridge's Patent AU 607822 being used for a clever “Spin ControlDifferential” for vehicles. This Patent is now assigned to me. There isthe option of having automatically reversing one way clutches if reversedirection of the load is required and motor braking is needed. Howeverif required a motor brake one way clutch may be fitted between the inputshaft and output of the gearing. The rollers will rotate about there ownaxis as they move in relation to the scallops. The bearing (18), isadded to eliminate the sliding action of roller (20) against cam (17),which would occur (if they were in direct contact) because of thedifference in their circumferential speeds. The output (21) isconstrained to rotate about the central axis of the input shaft (13).The cyclical movement of the rollers (20) acting on the scallops alone,causes the output (21) to rotate at a reduced rotational speed dependingon the number of rollers and scallops.

For example, if the cage (22) is constrained from being able to rotate,and if assembly 11 has four rollers (20), and there are five scallops inthe output (21), the ratio would be one output (21) revolution for everyfive revolutions of the cam (17) with the output (21) rotating in thesame direction as the cam (17).

Assembly 12 is the second unequal coaxial assembly and comprises of arotor (15), cam (16), and rollers (19). The scallops in the second ringgear 45 make contact with the rollers (19) which make contact with thecam (16). The cam (16) is fixed to the rotor (15) (Now shown as aninternal clutch drum). To reduce frictional losses, a bearing would befitted to the outside diameter of the cam (16). The number of scallopsand rollers for assembly 12 are different to the numbers for assembly11. The rollers are located in equally spaced guides in the cage (22).The cage therefore bridges axially between assemblies 11 and 12 and therollers (19) are constrained to rotate at the same angular velocityabout the central axis of the input shaft (13) as the rollers. (20) ofassembly 11. The numbers of scallops and rollers are such that if thecage (22) is held relative to the frame (26), the internal ring gear(45)tends to cause the cam (16) to rotate with an angular velocity in theopposite direction to cam (17).

For example, if the cage (22) is constrained from being able to rotate,and if assembly 12 has four rollers (20), and there are three scallopsin the internal ring-gear body 45, the ratio would be one internal ringgear 45 revolution for every three revolutions of the cam (16), with theinternal ring gear 45 rotating in the opposite direction to the cam(16).

If the assembly 11 cam (17) is caused to rotate, the output (21) willrotate at another angular velocity, being a fixed ratio to the inputangular velocity. The assembly 12 cam (16) will rotate at an angularvelocity dependent on the fixed ratio of assembly 12, and for thecentral concept of the present invention, in the opposite direction tocam (17). If assembly 12 was arranged so that cam (16) rotated in thesame direction as cam (17), the output would be reversed if cam (16) wasbraked. The cam (16) will have no effect on the output angular velocityuntil the electrical coils of items 24 are activated. With theelectrical coils activated, a torque is transmitted through the rotor(15) to the cam (16). The electrical coils could be activated so thatthe torque acts in the same or opposite direction as the rotation of thecam (16). If the torque acts in the same direction as the rotation ofthe cam (16), the output would rotate at the angular velocity determinedby the fixed ratio but with an increased torque dependant on the amountof torque contributed by items 24.

The torque from items 24 act in the opposite direction of rotation ofthe cam (16) (ie. the same direction as the input shaft (13)). In thiscase, assembly 12 will act so as to try and cause the output (21), torotate in the opposite direction and the cage (22) in the same directionas the input. In simplistic terms, the opposite actions on the outputand cage caused by cam (16) tend to ‘lock’ the cage (22) to the inputrotation. The cage (22) is free to rotate in the direction of the input(cam (17)). The cage (22) therefore tends to cause the output (21) torotate as one with the input. The rollers (20) rotation about thecentral axis of the input shaft (13) due to the action of the cam (17),has superimposed on it a rotation about this central axis due to therotation of the cage (22) in the direction of the input. It is thissuperimposed rotation that causes the output to increase its angularvelocity relative to the input angular velocity. The amount of rotationof the cage (22) and therefore, the amount of superimposed rotation isdetermined by the relative differences in the output resistive torque(hereafter called the ‘load’) and the input torque from cam (17) anditems 24. (If an internal or external hybrid input is appliedconcentrically about the input shaft 13 to this 15 rotor shown nowinstead of a motor rotor, is shown as a clutch drum this would have thesame effect as 24 being electrically driven, and indeed this isconcentrically accessible). When the ‘load’ lowers relatively and thetorque from items 24 is increased, the less the torque required from cam(17). As the proportion of torque, from cam (16) relative to cam (17)increases, the more the output (21) tends to be ‘locked’ to the inputand the more the ratio of input to output angular velocity tends toapproach 1:1. The output gear ratio therefore can be progressivelydecreased from the fixed ratio of the first assembly to a 1:1 ratio byprogressively increasing the torque acting on the cam (16) from zero toa value that causes the cage (22) to be ‘locked’ fully to the input. Theoutput torque is inversely proportional to the output angular velocity.

FIG. 2 shows another embodiment of a “eM Dean” Gear, in this case thereis a combination of a module 10 with extensions (on the right-hand half)that enable further multiple fixed ratios to be obtained from the oneeMDean Gear The module 10 shows the central concept of the presentinvention. The input is via a separate motive source (not shown) actingthrough the input shaft (13). The output is the ring element or body(21). However many new options are available if there is the addedextension FIG. 2 (For example there is now the option of a secondinternal body ring-gear with added cam on the right hand side which canbe actuated by optionally removing the two bolts and allowing the newsecond internally shown with arrows. The ring-gear with output 51 canthen itself drive another cage with a cam coupled to it so as to providesuch as over-drive features. Another cage/cam is shown able to be drivenwhich can provide reversing features by breaking it from being operatingin a forward direction of the chosen output. There are also abilities tochange ratios or other features by concentrically moving any concentricshafts in and out as shown on 50 and 52.

The first unequal coaxial assembly comprises of a cam {sun-gear} (17),and rollers {planet-gears} (20) and the ring element or body (21). Thecam (17) is fixed to the input shaft (13). The outer diameter of the cam(17) makes contact with the rollers (20). As the input rotates, the cam(17) outer diameter moves in an eccentric fashion. This causes therollers (20) to be cyclically displaced away and towards the centralaxis of the “eM Dean” Gear as also described in the “A Converter” priorPatent AU 742781 and A 35198/01, explaining the advance here asfollows—“the total displacement relative to this central axis, beingtwice the cam axis offset from this axis. The rollers (20) are locatedin equally spaced guides in the cage {planet carrier} (22). The rollers(20) make contact with scallops in the output (21). For both assemblies(11 & 12), the number of scallops relative to the number rollers incontact with the scallops, determines the direction of rotation it wouldrotate the output (21) if the cage (22) was held still. One more scallopthan the number of rollers gives an output rotation direction the sameas the cam rotation. One less scallop than the number of rollers wouldgive an output rotation the opposite to the cam rotation. The scallopsare so shaped that as the rollers are acted on by the cam, the scallopsrotate relative to the cage at a constant angular velocity ratio to thatof the cam. The action between the cam (17), bearing (18) and rollers(20) against the output (21), causes an equal and opposite reaction onthe cage (22), tending to rotate it in the opposite direction to therotation of the output (21).

The cage (22) is constrained by a rotation blocking means in such a wayas to allow the cage (22) to only rotate in a direction the same as theoutput (21). Therefore because of the reactive forces, the cage (22)will be held against the rotation blocking means and will therefore bestationary relative to the frame (the structure holding mounting themotor etc.) with just the actions of assembly 11 alone. The rollers willrotate about there own axis as they move in relation to the scallops. Abearing could be fitted to the outside diameter of the cams (16 & 17) toeliminate the sliding action of roller (19 & 20) against cam (16 & 17),which would occur (if they were in direct contact) because of thedifference in their circumferential speeds. The output (21) isconstrained to rotate about the central axis of the input shaft (13).The cyclical movement of the rollers (20) acting on the scallops alone,causes the output (21) to rotate at a reduced rotational speed dependingon the number of rollers and scallops.

For example, if the cage (22) is constrained from being able to rotate,and if assembly 11 has four rollers (20), and there are five scallops inthe output (21), the ratio would be one output (21) revolution for everyfive revolutions of the cam (17) with the output (21) rotating in thesame direction as the cam (17).

The second unequal coaxial assembly comprises of a cam (16), and rollers(19) and inner body (45) The scallops in the body (45) make contact withthe rollers (19) which make contact with the cam (16). The number ofscallops and rollers for the assembly are different to the firstassembly 11. The rollers are located in equally spaced guides in the,cage (22). The cage therefore bridges axially between assemblies 11 and12 and the rollers (19) are constrained to rotate at the same angularvelocity about the central axis of the input shaft (13) as the rollers(20) of assembly 11. The numbers of scallops and rollers are such thatif the cage (22) is held relative to the frame, the body (45) tends tocause the cam (16) to rotate with an angular velocity in the oppositedirection to cam (17).

For example, if the cage (22) is constrained from being able to rotate,and if assembly 12 has four rollers (20), and there are three scallopsin the body (45), the ratio would be one body (45) revolution for everythree revolutions of the cam (16), with the body (45) rotating in theopposite direction to the cam (16).

If the assembly 11 cam (17) is caused to rotate, the body (45) willrotate at another angular velocity, being a fixed ratio to the inputangular velocity. The assembly 12 cam (16) will rotate at an angularvelocity dependent on the fixed ratio of assembly 12, and for thecentral concept of the present invention, in the opposite direction tocam (17). If assembly 12 was arranged so that cam (16) rotated in thesame direction as cam (17), the output would be reversed if cam (16) wasbraked. The cam (16) will have no effect on the output angular velocityuntil a torque is made to act on it. Any torque acting on cam (16) couldact in the same or opposite direction as, the rotation of the cam (16).If the torque acts in the same direction, the output would rotate at theangular velocity determined by the fixed ratio but with an increasedtorque. As in the previous embodiment the torque acting on cam (16) isin a direction opposite to that of the rotation of the cam (16) (ie. thesame direction as the input shaft (13)). In this case, assembly 12 willact so as to try and cause the inner body (45), to rotate in theopposite direction and the cage (22) in the same direction as the input.In simplistic terms, the opposite actions on the output and cage causedby cam. (16) tend to ‘lock’ the cage (22) to the input rotation. Thecage (22) is free to rotate in the direction of the input (cam (17)).The cage (22) therefore tends to cause the output (21) to rotate as onewith the input. The rollers (20) rotation about the central axis of theinput shaft (13) due to the action of the cam (17), has superimposed onit a rotation about this central axis due to the rotation of the cage(22) in the direction of the input. It is this superimposed rotationthat causes the output to increase its angular velocity relative to theinput angular velocity. The amount of rotation of the cage (22) andtherefore the amount of superimposed rotation is determined by therelative differences in the output resistive torque (hereafter calledthe ‘load’) and the input torque from the cams (17 & 16). When the‘load’ lowers relatively and the torque acting on cam (16) is increased,the less is the torque required from cam (17). As the proportion oftorque from cam (16) relative to cam (17) increases, the more the output(21) tends to be ‘locked’ to the input and the more the ratio of inputto output angular velocity tends to approach 1:1. The output gear ratiotherefore can be progressively decreased from the fixed ratio of thefirst assembly to a 1:1 ratio by progressively increasing the torqueacting on the cam (16) from zero to a value that causes the cage (22) tobe ‘locked’ fully to the input. The output torque is inverselyproportional to the output angular velocity.

The input torque to cam (16) can be through another motive source or aclutch mechanism connecting the input shaft (13) to the extension of cam(16). If a clutch mechanism was used, the control mechanism could beautomatic and linked to the output speed through the use of acentrifugal clutch. With a centrifugal clutch arrangement, as the speedof the output increases the clutch engages and tends to turn cam (16) inthe same direction as the input, cam (17). So as the output isaccelerated at the lower fixed ratio, there will come a stage when theinput shaft is spinning at such a speed that the centrifugal clutchstarts to engage. As the centrifugal clutch engages, the output gearratio would progressively decrease to 1:1.

With the addition of other rotation blocking means to this arrangementto constrain other parts to rotate in one direction only, there is thepossibility of having sequentially selected multiple ratios with otheroutputs. For example if the rotation blocking means is connected to cam(16), (or other especially designed cages or ring gears with cams canprovide unlimited features) of the transmission the output will be thebody (21) or (51), There is also the option of arranging the cage (22)so that it protrudes from the right-hand side of FIG. 2. The cam (16)can have an extension and its rotation could be controlled by variousexternal or internal means.

Whilst the above has been given by way of illustrative example of thepresent invention many variations and modifications thereto will beapparent to those skilled in the art without departing from the broadambit and scope of the invention as herein set out in the appendedclaims.

1. A transmission having-at least one input and one output and being ofthe epicyclic type involving interaction of three mechanically distinctrotating elements with any suitable form that allows the transfer oftorque between input and output, namely a sun element, a ring elementand a planet element in each of at least first and second unequalco-axial epicyclic assemblies, a first element of the first assembly anda first element of the second assembly able to rotate independently, thefirst rotating element of the second assembly able to be within thefirst rotating element of the first assembly, a second rotating element,of the first assembly and a second rotating element of the secondassembly being constrained to rotate at a common angular velocity, athird element of the first assembly being connected to a motive source,and control means for progressively changing the gear-ratio applied to aload connected to the first element of the first assembly of thetransmission characterised in that the first and second assemblies eachrepresent unequal fixed gear ratios respectively between the input andthe output of the “eM Dean” Gear, the first and second assembliesarranged so that if individually each assembly has their first elementconstrained and their third element rotated in a certain direction thesecond element will try to rotate in an opposite direction relative tothe tendency of the other assembly, the control means being operative toprogressively increase or decrease the output gear ratio in accordancewith the demand for an output lower or higher gear stage of operation.2. A transmission according to claim 1 wherein the first elements arethe ring elements of the respective assemblies, the ring elements beingouter bodies having spaced endless scallop guides being adapted toreceive sets of planet elements being in the form of rollers, the secondrotating elements comprising of planet carrier elements and planetelements, the planet carrier elements of the respective assembliesconstrained to rotate about an axis collinear with the axes of theirrespective third elements, the planet carrier elements locating andcontrolling the motion of integral spaced sets of rollers correspondingto the planet elements of each assembly, the rollers bridging betweenthe scallop guides of the outer bodies and the third elements of theassemblies, the planet carrier elements being constrained by a rotationcontrolling means allowing free rotation in one direction and acontrolled rotation in the other direction, the third elements of theassemblies being sun elements in the form of respective cams.
 3. Atransmission according to claim 1 wherein the first elements are thering elements of the respective assemblies, the second rotating elementscomprising of planet carrier elements and planet elements, the planetcarrier elements of the respective assemblies constrained to rotateabout an axis collinear with the axes of their respective thirdelements, the planet elements constrained to rotate on their own axeswith the axes being constrained to rotate with the planet carrierelement, the planet elements with their axes offset from theirrespective planet carrier element so as to bridge individually or incombination with other planet elements between the ring element and thethird element of their respective assembly, the planet carrier elementsbeing constrained by a rotation controlling means allowing free rotationin one direction and a controlled rotation in the other direction, thethird elements of the assemblies being sun elements, the ring and planetand sun elements being in a form that will allow the transfer of torqueat a fixed ratio between elements.
 4. A transmission according to claim2 wherein the first elements are the ring elements of the respectiveassemblies, the ring elements being outer bodies having spaced endlessscallop guides being adapted to receive sets of planet elements being inthe form of rollers, the second rotating elements comprising of planetcarrier elements and planet elements, the planet carrier elements of therespective assemblies constrained to rotate about an axis collinear withthe axes of their respective third elements, the planet carrier elementslocating and controlling the motion of integral spaced sets of rollerscorresponding to the planet elements of each assembly, the rollersbridging between the scallop guides of the outer bodies and the thirdelements of the assemblies, the planet carrier elements beingconstrained by a rotation controlling means allowing free rotation inone direction and a controlled rotation in the other direction, thethird elements of the assemblies being sun elements in the form ofrespective cams, the control means being operable to supply a variablerotation to the third element of the second assembly across a continuousrange of output gear ratios between low and high angular velocities atrespective predetermined low and high output angular velocities.
 5. Thetransmission according to claim 3 wherein the first elements are thering elements of the respective assemblies, the second rotating elementscomprising of planet carrier elements and planet elements, the planetcarrier elements of the respective assemblies constrained to rotateabout an axis collinear with the axes of their respective thirdelements, the planet elements constrained to rotate on their own axeswith the axes being constrained to rotate with the planet carrierelement, the planet elements with their axes offset from theirrespective planet carrier element so as to bridge individually or incombination with other planet elements between the ring element and thethird element of their respective assembly, the planet carrier elementsbeing constrained by a rotation controlling means allowing free rotationin one direction and a controlled rotation in the other direction, thethird elements of the assemblies being sun elements, the ring and planetand sun elements being in a form that will allow the transfer of torqueat a fixed ratio between elements, the control means being operable tosupply a variable rotation to the third element of the second assemblyacross a continuous range of output gear ratios between low and highangular velocities at respective predetermined low and high outputangular velocities.
 6. A transmission according to claim 2 wherein thefirst elements are the ring elements of the respective assemblies, thering elements being outer bodies having spaced endless scallop guidesbeing adapted to receive sets of planet elements being in the form ofrollers, the second rotating elements comprising of planet carrierelements and planet elements, the planet carrier elements of therespective assemblies constrained to rotate about an axis collinear withthe axes of their respective third elements, the planet carrier elementslocating and controlling the motion of integral spaced sets of rollerscorresponding, to the planet elements of each assembly, the rollersbridging between the scallop guides of the outer bodies and the thirdelements of the assemblies, the planet carrier elements beingconstrained by a rotation controlling means allowing free rotation inone direction and a controlled rotation in the other direction, thethird elements of the assemblies being sun elements in the form ofrespective cams, the first element of the second assembly constrained toa fixed frame of reference, a third element of the second assemblyrotating at a controlled angular velocity the control means beingoperative to progressively increase or decrease the output gear ratio inaccordance with the demand for an output lower or higher gear stage ofoperation.
 7. A transmission according to claim 3 wherein the firstelements are the ring elements of the respective assemblies, the secondrotating elements comprising of planet carrier elements and planetelements, the planet carrier elements of the respective assembliesconstrained to rotate about an axis collinear with the axes of theirrespective third elements, the planet elements constrained to rotate ontheir own axes with the axes being constrained to rotate with the planetcarrier element, the planet elements with their axes offset from theirrespective planet carrier element so as to bridge individually or incombination with other planet elements between the ring element and thethird element of their respective assembly, the planet carrier elementsbeing constrained by a rotation controlling means allowing free rotationin one direction and a controlled rotation in the other direction, thethird elements of the assemblies being sun elements, the ring and planetand sun elements being in a form that will allow the transfer of torqueat a fixed ratio between elements, the first element of the secondassembly constrained to a fixed frame of reference, a third element ofthe second assembly rotating at a controlled angular velocity thecontrol means being operative to progressively increase or decrease theoutput gear ratio in accordance with the demand for an output lower orhigher gear stage of operation.
 8. A transmission according to claim 2wherein the first elements are the ring elements of the respectiveassemblies, the ring elements being outer bodies having spaced endlessscallop guides being adapted to receive sets of planet elements being inthe form of rollers, the second rotating elements comprising of planetcarrier elements and planet elements, the planet carrier elements of therespective assemblies constrained to rotate about an axis collinear withthe axes of their respective third elements, the planet carrier elementslocating and controlling the motion of integral spaced sets of rollerscorresponding to the planet elements of each assembly, the rollersbridging between the scallop guides of the outer bodies and the thirdelements of the assemblies, the planet carrier elements beingconstrained by a rotation controlling means allowing free rotation inone direction and a controlled rotation in the other direction, thethird elements of the assemblies being sun elements in the form ofrespective cams, the first element of the second assembly constrainedfrom rotating in one direction by a fixed frame of reference and free torotate in the other direction.
 9. A transmission according to claim 3wherein the first elements are the ring elements of the respectiveassemblies, the second rotating elements comprising of planet carrierelements and planet elements, the planet carrier elements of therespective assemblies constrained to rotate about an axis collinear withthe axes of their respective third elements, the planet elementsconstrained to rotate on their own axes with the axes being constrainedto rotate with the planet carrier element, the planet elements withtheir axes offset from their respective planet carrier element so as tobridge individually or in combination with other planet elements betweenthe ring element and the third element of their respective assembly, theplanet carrier elements being constrained by a rotation controllingmeans allowing free rotation in one direction and a controlled rotationin the other direction, the third elements of the assemblies being sunelements, the ring and planet and sun elements being in a form that willallow the transfer of torque at a fixed ratio between elements, thefirst element of the second assembly constrained from rotating in onedirection by a fixed frame of reference and free to rotate in the otherdirection.
 10. A transmission according to claim 2 wherein the firstelements are the ring elements of the respective assemblies, the ringelements being outer bodies having spaced endless scallop guides beingadapted to receive sets of planet elements being in the form of rollers,the second rotating elements comprising of planet carrier elements andplanet elements, the planet carrier elements of the respectiveassemblies constrained to rotate about an axis collinear with the axesof their respective third elements, the planet carrier elements locatingand controlling the motion of integral spaced sets of rollerscorresponding to the planet elements of each assembly, the rollersbridging between the scallop guides of the outer bodies and the thirdelements of the assemblies, the planet carrier elements beingconstrained by a rotation controlling means allowing free rotation inone direction and a controlled rotation in the other direction, thethird elements of the assemblies being sun elements in the form ofrespective cams, the third element of the second assembly beingconstrained to rotate at a respective fixed gear ratio relative to aninput to the “eM Dean Gear, the control means being operable to supply avariable rotation to the first element of the second assembly across acontinuous range of output gear ratios between low and high angularvelocities at respective predetermined low and high output angularvelocities.
 11. A transmission according to claim 3 wherein the firstelements are the ring elements of the respective assemblies, the secondrotating elements comprising of planet carrier elements and planetelements, the planet carrier elements of the respective assembliesconstrained to rotate about an axis collinear with the axes of theirrespective third elements, the planet elements constrained to rotate ontheir own axes with the axes being constrained to rotate with the planetcarrier element, the planet elements with their axes offset from theirrespective planet carrier elements so as to bridge individually or incombination with other planet elements between the ring element and thethird element of their respective assembly, the planet carrier elementsbeing constrained by a rotation controlling means allowing free rotationin one direction and a controlled rotation in the other direction, thethird elements of the assemblies being sun elements, the ring and planetand sun elements being in a form that will allow the transfer of torqueat a fixed ratio between elements, the third element of the secondassembly being constrained to rotate at a respective fixed gear ratiorelative to an input to the transmission, the control means beingoperable to supply a variable rotation to the first element of thesecond assembly across a continuous range of output gear ratios betweenlow and high angular velocities at respective predetermined low and highoutput angular velocities.
 12. A transmission according to claim 2wherein the first elements are the ring elements of the respectiveassemblies, the ring elements being outer bodies having spaced endlessscallop guides being adapted to receive sets of planet elements being inthe form of rollers, the second rotating elements comprising of planetcarrier elements and planet elements, the planet carrier elements of therespective assemblies constrained to rotate about an axis collinear withthe axes of their respective third elements, the planet carrier elementslocating and controlling the motion of integral spaced sets of rollerscorresponding to the planet elements of each assembly, the rollersbridging between the scallop guides of the outer bodies and the thirdelements of the assemblies, the planet carrier elements beingconstrained by a rotation controlling means allowing free rotation inone direction and a controlled rotation in the other direction, thethird elements of the assemblies being sun elements in the form ofrespective cams, the third element of the second assembly beingconstrained to rotate at a respective fixed gear ratio relative to aninput to the transmission, the flow of a suitably formulated fluid orgas or like due to the action of the first element of the secondassembly against a fixed frame of reference being directed andcontrolled in two circuits, the flow of said suitably formulated fluidor gas or like from the said first element of the second assembly in thefirst circuit being directed and controlled towards the contractingspaces on one side of the rollers of the first assembly so as to tend torestrict the movement of the rollers within the scallops of the firstelement of the first assembly, the flow of said suitably formulatedfluid or gas or like in the second circuit being directed and controlledtowards a part of the a transmission that provides a low resistance toflow, the progressive control of the amount of flow of the said suitablyformulated fluid or gas or like in the first and second circuitsoperable to progressively change the gear ratio applied to a loadconnected to the first element of the first assembly of the VariableRatio Multi-gear.
 13. A transmission according to claim 10 whereinenergy can be transferred to the suitably formulated fluid or gas orlike and stored internally or externally so as to enable the return ofthe energy to the load when required.
 14. A transmission according toclaim 2 wherein the first elements are the ring elements of therespective assemblies, the ring elements being outer bodies havingspaced endless scallop guides being adapted to receive sets of planetelements being in the form of rollers, the second rotating elementscomprising of planet carrier elements and planet elements, the planetcarrier elements of the respective assemblies constrained to rotateabout an axis collinear with the axes of their respective thirdelements, the planet carrier elements locating and controlling themotion of integral spaced sets of rollers corresponding to the planetelements of each assembly, the rollers bridging between the scallopguides of the outer bodies and the third elements of the assemblies, theplanet carrier elements being constrained by a rotation controllingmeans allowing free rotation in one direction and a controlled rotationin the other direction, the third elements of the assemblies being sunelements in the form of respective cams, the rotation of the thirdelements causing motion of the second rotating elements, the motion ofthe second and third elements causing contracting and expanding spaces,the contracting spaces in the first assembly displacing a suitablyformulated fluid or gas or like, the displaced fluid or gas or likebeing directed into and controlled in two circuits, the control meansproportioning the flow of said suitably formulated fluid or gas or likein the said two circuits in accordance with the demand for an outputlower or higher gear stage of operation, the flow of said suitablyformulated fluid or gas or like in the first circuit being used torotate the third element of the second assembly, the flow of saidsuitably formulated fluid or gas or like in the second circuit beingdirected and controlled towards a part of the transmission that providesa low resistance to flow, the suitably formulated fluid or gas or likebeing drawn into the expanding spaces of the first assembly in acontrolled manner after completing the first or second circuits, theprogressive control of the amount of flow of the said suitablyformulated fluid or gas or like in the first and second circuitsoperable to progressively change the gear ratio applied to a loadconnected to the first element of the first assembly of the VariableRatio Multi-gear.
 15. A transmission according to claim 12 whereinenergy can be transferred to the suitably formulated fluid or gas orlike and stored internally or externally so as to enable the return ofthe energy to the load when required.
 16. A transmission according toclaim 1 wherein the axis of the input or inputs are collinear with theaxis of the third element of the first assembly, the axis of the outputor outputs are collinear with the axis of the third element of the firstassembly, the axis of the third elements of the first and secondassemblies are collinear, the elements of both assemblies supporteddirectly or indirectly by the fixed frame of reference, the motivesource supported directly or indirectly by the fixed frame of reference,the reactive torque from the motive source acting on the fixed frame ofreference.
 17. A transmission according to claim 1 wherein the axis ofthe inputs are collinear with the axis of the third element of the firstassembly, the axis of the output or outputs are collinear with the axisof the third element of the first assembly, the axis of the thirdelements of the first and second assemblies are collinear, the elementsof both assemblies supported directly or indirectly by the fixed frameof reference, a motive source supported directly or indirectly by thefixed frame of reference and connected to the third element of the firstassembly, another motive source supported directly or indirectly by thefixed frame of reference and connected to the third element of thesecond assembly, the reactive torques from the motive sources acting onthe fixed frame of reference.
 18. A transmission according to claim 1wherein the axis of the inputs are collinear with the axis of the thirdelement of the first assembly, the axis of the output or outputs arecollinear with the axis of the third element of the first assembly, theaxis of the third elements of the first and second assemblies arecollinear, the elements of both assemblies supported directly orindirectly by the fixed frame of reference, an input driven by externalinfluences such as wind connected to the third element of the firstassembly, another input source driven by external influences andconnected to the third element of the second assembly.
 19. Atransmission having an input and two contra-rotating outputs and beingof the epicyclic type involving interaction of three mechanicallydistinct rotating elements with any suitable form that allows thetransfer of torque between input and output, namely a sun element, aring element and a planet element being in each of at least first,second and third co-axial epicyclic assemblies, a second rotatingelement of the first assembly and a second rotating element of thesecond assembly being constrained to rotate at a common angularvelocity, the first element of the first assembly and the first elementof the third assembly being constrained to rotate at a common angularvelocity, and control means for progressively changing the gear ratioapplied to a load connected to the first element of the first and thirdassemblies and another load connected to the second element of the thirdassembly of the Variable Ratio Multi-gear characterised in that thefirst and second assemblies each represent unequal fixed gear ratiosrespectively between the input and the output of the Variable RatioMulti-gear the first and second assemblies arranged so that ifindividually each assembly has their first element constrained and theirthird element rotated in a certain direction the second element willtend to rotate in an opposite direction relative to the tendency of theother assembly, the third assembly arranged so that if individually it'sfirst element is constrained and the third element rotated in the samecertain direction of the first and second assemblies the second elementwill tend to rotate in the same direction as the second assembly, thecontrol means being operative to progressively increase or decrease theoutput gear ratios in accordance with the demand for an output lower orhigher gear stage of operation.
 20. A transmission according to claim 1wherein more elements can be included to provide overdrive speed anddirectional reversing features to a load coupled to the first element ofthe first assembly.
 21. A transmission according to claim 1 wherein therotation blocking and controlling means required can provide energystorage able to be re used, with mechanical or pressure accumulation.22. A transmission according to claim 1 wherein the rotation blockingand controlling means can provide motor braking by automaticallyreversible one way clutches working in sequence for internally accessingcarrier or ring-gear restricting.
 23. A transmission according to claim1 where the compact “Torque Multiplier” action may be accessed bysequentially controlling the storage of energy, internally orexternally.
 24. A transmission according to claim 1 where the control ofthe load and with internal or external remote control such as betweenthe first and the second and third elements of the second assembly canbe activated by electro-magnetic, magnetic fields, or electro highvoltage to activating suitable contents such as Liquid Polymers inSilicon oil.
 25. A transmission according to claim 1 where reactivefeedback from the load is used to automatically stabilise mobiletransport.
 26. A transmission according to claim 1 where sophisticatedelectronic sensors are placed in strategic positions such asgravitational and tilt Sensors used to incorporate self stabilising toover ride mechanically fed back reaction from tilting of vehicles.
 27. Atransmission according to claim 1 where multiple configurations of thisGearing can be linked together to perform three dimensional manipulationsuch as to interact and integrate the Camber Control with the Castercontrol as shown in FIG. 5 (lower) and FIG. 12 with reference to FIG.
 3028. A transmission according to claim 1 where a number of cages able torotate about the first axis and each cage wholly or partially enclosedby the body, means between the central shaft and any number of thecages, means between the body and any number of the cages, means betweenthe cages in any sets of combinations of any of the cages, wherein eachinput and each output is applied to or taken from one of the body, thecentral shaft and any number of the cages, and application of a firsttorque to the central shaft causing the central shaft to rotate aboutthe axis while torques are applied, about the first axis, to any numberof the cages will cause at least one of the cages, cams (sun-gears) andthe body to rotate and, furthermore, variation of one of the torquesbetween zero and a maximum value will cause a variation of the ratio ofthe angular velocities of the central shaft and the body through theactions of the means.
 29. A transmission according to claims 1 to 30substantially as described herein
 30. A transmission according to claims1-34 substantially as described herein with reference to any one or moreof the accompanying drawings.